CN203430906U - Hydraulic buffering driving and buffering braking device - Google Patents
Hydraulic buffering driving and buffering braking device Download PDFInfo
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- CN203430906U CN203430906U CN201320322031.XU CN201320322031U CN203430906U CN 203430906 U CN203430906 U CN 203430906U CN 201320322031 U CN201320322031 U CN 201320322031U CN 203430906 U CN203430906 U CN 203430906U
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Abstract
The utility model belongs to the field of parts of vertical or swing lifting systems, and particularly relates to a hydraulic buffering driving and buffering braking device. The hydraulic buffering driving and buffering braking device comprises an energy accumulator (16) and a hydraulic cylinder (17). The hydraulic cylinder (17) comprises a hydraulic cylinder barrel (11), a hydraulic cylinder piston rod (13) and a hydraulic cylinder piston (10) arranged on the front portion of the hydraulic cylinder piston rod (13); a hydraulic one-way valve (18) is arranged at the bottom of the hydraulic cylinder barrel (11); a hydraulic cylinder barrel tail buffering cavity (5) is formed by the radial surface of the tail of the hydraulic cylinder piston rod (13) and the radial surface of the central concave area at the bottom of the hydraulic cylinder barrel (11); one port of the hydraulic cylinder barrel tail buffering cavity (5) is communicated with oil inlet ports of a tubular hydraulic anti-explosion valve, the energy accumulator (16) and the hydraulic one-way valve (18); and the other port of the hydraulic one-way valve (18) is communicated with a hydraulic cylinder rodless cylinder (9). The hydraulic buffering driving and buffering braking device is simple in structure, good in buffering effect, stable in performance, simple to operate, and low in construction cost.
Description
Technical field
The utility model belongs to vertically or swings hydraulic lifting system accessory field, relates in particular to a kind of hydraulic cushion driving, buffer brake device.
Background technique
In prior art, when vertically (or swing) elevator mechanism arbitrary position in decline process of common Driven by Hydraulic Cylinder device stops, because buffering impact is not large, can cause like this equipment to damage too early, the health of Hai Huigeisui mechanism players causes fatal harm.In order to reduce this impact, as long as operating mode allows just to reduce braking impact by reducing rate of descent.And the oil hydraulic cylinder that rate of descent requires piece must increase electromagnetic speed-adjusting valve cooperation head and the tail band buffering is realized the first reduction of speed before braking, or directly selection percentage selector valve is realized buffer-braking.When decline buffer-braking selects electromagnetic speed-adjusting valve to coordinate the oil hydraulic cylinder of head and the tail band buffering, the delay time of electrical control coordinates electromagnetic speed-adjusting valve, and this System Working Principle is simple, but debugging difficulty is high, and the effect recalling is unstable; And selection percentage selector valve is realized the scheme of buffer-braking, its cost is high, and most users is difficult to accept.
Model utility content
The utility model is intended to overcome the deficiencies in the prior art part and provides a kind of simple in structure, good buffer effect, and stable performance, simple to operate, cheap hydraulic cushion drives, buffer brake device.
For solving the problems of the technologies described above, the utility model is to realize like this.
Driving, a buffer brake device, it comprises accumulator and oil hydraulic cylinder.Described oil hydraulic cylinder comprises hydraulic cylinder, hydraulic cylinder piston rod and is assigned in the hydraulic cylinder piston of hydraulic cylinder piston rod front portion; In described hydraulic cylinder bottom, is furnished with hydraulically-controlled one-way valve; The radial surface of the radial surface of described hydraulic cylinder piston rod afterbody and hydraulic cylinder bottom centre sunk area forms hydraulic cylinder afterbody buffer cavity; The port of described hydraulic cylinder afterbody buffer cavity communicates with the oil-feed port of tubular type hydraulic pressure explosion-proof valve, accumulator and hydraulically-controlled one-way valve respectively; The another port of described hydraulically-controlled one-way valve communicates with oil hydraulic cylinder rodless cavity.
As a kind of preferred version, accumulator described in the utility model comprises accumulator inflated with nitrogen chamber, is placed in accumulator piston and accumulator oil-filled chamber in accumulator; Described accumulator oil-filled chamber communicates with hydraulic cylinder afterbody buffer cavity.
As another kind of preferred version, hydraulically-controlled one-way valve described in the utility model comprises check valve spring seat, check valve spring and steel ball; Described check valve spring is placed on check valve spring seat, and the hydraulic oil at hydraulic cylinder afterbody buffer cavity place enters oil hydraulic cylinder rodless cavity by steel ball and check valve spring seat.
Further, the port of accumulator described in the utility model communicates with the port of hydraulic cylinder afterbody buffer cavity through high pressure hose or seamless steel pipe.
Further, the utility model throttle valve in parallel on described hydraulically-controlled one-way valve; One end hydraulic fluid port of described throttle valve communicates with oil hydraulic cylinder rodless cavity, and its other end communicates with hydraulic cylinder afterbody buffer cavity.
In addition, accumulator described in the utility model also can adopt bladder type hydropneumatic accumulator.
The utility model cushioning effect is obvious, stable performance, and debugging is simple, cheap.The utility model can substitute common ratio hydraulic system, and cost performance is far away higher than ratio hydraulic system.The utility model can make vertically or oscillating lifting system, in the starting stage of rising, without obvious play phenomenon, before dropping to minimum point, has obvious deceleration.When the arbitrary position in vertical or oscillating lifting system total travel movement process stops, can guaranteeing that elevating system is subject to minimum impact.The utility model can be used in recreation facility " interplanetary travel ", every interplanetary travel recreation facility configuration 12 covering devices, and every covering device drives a large arm to do oscillating lifting motion.
Accompanying drawing explanation
Below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.Protection domain of the present utility model is not only confined to the statement of following content.
Fig. 1 is the utility model overall structure schematic diagram.
Fig. 2 is that the utility model hydraulic cylinder piston rod tail end is near the process overall structure schematic diagram of retracting before hydraulic cylinder afterbody buffer cavity.
Fig. 3 is that the utility model hydraulic cylinder piston rod stretches out while starting moment running of hydraulic power oil view.
Fig. 4 view when to be the utility model hydraulic cylinder piston rod tail end stop near the process arbitrary position of retracting before hydraulic cylinder afterbody buffer cavity.
Fig. 5 is that the utility model hydraulic cylinder piston rod stretches out after startup to tail end and leaves running of hydraulic power oil view during hydraulic cylinder afterbody buffer cavity.
Fig. 6 is the utility model hydraulic cylinder piston rod running of hydraulic power oil view while entering after hydraulic cylinder afterbody buffer cavity buffer-braking.
Fig. 7 is that the utility model hydraulic cylinder piston rod leaves hydraulic cylinder afterbody buffer cavity running of hydraulic power oil view afterwards.
Fig. 8 is that the utility model hydraulic cylinder piston rod leaves after hydraulic cylinder afterbody buffer cavity view when arbitrary position stops.
In figure: 1, accumulator inflated with nitrogen chamber; 2, accumulator piston; 3, accumulator oil-filled chamber; 4, accumulator oil hydraulic cylinder connecting tube; 5, hydraulic cylinder afterbody buffer cavity; 6, check valve spring seat; 7, check valve spring; 8, steel ball; 9, oil hydraulic cylinder rodless cavity; 10, hydraulic cylinder piston; 11, hydraulic cylinder; 12, oil hydraulic cylinder rod chamber; 13, hydraulic cylinder piston rod; 14, hydraulic cylinder guide sleeve; 15, hydraulic cylinder guide sleeve gland; 16, accumulator; 17, oil hydraulic cylinder; 18, hydraulically-controlled one-way valve; 19, oil sump tank hydraulic fluid port; 20, tubular type hydraulic pressure explosion-proof valve.
Embodiment
As shown in the figure, a kind of hydraulic cushion drives, buffer brake device, and it comprises accumulator 16 and oil hydraulic cylinder 17; Described oil hydraulic cylinder 17 comprises hydraulic cylinder 11, hydraulic cylinder piston rod 13 and is assigned in the hydraulic cylinder piston 10 of hydraulic cylinder piston rod 13 front portions; In described hydraulic cylinder 11 bottoms, is furnished with hydraulically-controlled one-way valve 18(certainly very according to design needs, also configurable hydraulic pressure one-way throttle valve, i.e. a throttle valve in parallel on the basis of former hydraulically-controlled one-way valve 18.); Sunk area in described hydraulic cylinder 11 bottom centre, at hydraulic cylinder piston rod 13, retract, when the afterbody of hydraulic cylinder piston rod 13 enters the sunk area of hydraulic cylinder bottom centre, the radial surface of the radial surface of described hydraulic cylinder piston rod 13 afterbodys and hydraulic cylinder 11 bottom centre's sunk areas forms hydraulic cylinder afterbody buffer cavity 5; The port of described hydraulic cylinder afterbody buffer cavity 5 communicates with the oil-feed port of tubular type hydraulic pressure explosion-proof valve, accumulator 16 and hydraulically-controlled one-way valve 18 respectively; The another port of described hydraulically-controlled one-way valve 18 communicates with oil hydraulic cylinder rodless cavity 9.
Accumulator 16 described in the utility model comprises accumulator inflated with nitrogen chamber 1, is placed in accumulator piston 2 and accumulator oil-filled chamber 3 in accumulator; Described accumulator oil-filled chamber 3 communicates with hydraulic cylinder afterbody buffer cavity 5.When the afterbody of hydraulic cylinder piston rod 13 enters the sunk area of hydraulic cylinder bottom centre, described accumulator oil-filled chamber 3 communicates with hydraulic cylinder afterbody buffer cavity 5, with the rodless cavity 9 of oil hydraulic cylinder be obstructed.
Hydraulically-controlled one-way valve described in the utility model comprises check valve spring seat 6, check valve spring 7 and steel ball 8; Described check valve spring 7 is placed on check valve spring seat 6, and the hydraulic oil at hydraulic cylinder afterbody buffer cavity 5 places enters oil hydraulic cylinder rodless cavity 9 by steel ball 8 and check valve spring seat 6, and reverse hydraulic oil can be ended by steel ball 8.
The port of accumulator 16 described in the utility model communicates with the port of hydraulic cylinder afterbody buffer cavity 5 through high pressure hose or seamless steel pipe.
The utility model can a throttle valve in parallel on described hydraulically-controlled one-way valve 18; One end hydraulic fluid port of described throttle valve communicates with oil hydraulic cylinder rodless cavity 9, and its other end communicates with hydraulic cylinder afterbody buffer cavity 5.
Accumulator 16 described in the utility model can adopt bladder type hydropneumatic accumulator.
Shown in Figure 1, the utility model comprises that accumulator and afterbody combine (accumulator with oil hydraulic cylinder between can adopt high pressure hose or seamless steel pipe to be connected) with the oil hydraulic cylinder of one-way buffer (containing one-way buffer effect adjustable type).The nitrogen pressure size of filling of accumulator is determined by the buffer-braking effect of load request.It is little that the utility model is applicable to start impact, and there is the applicable situation of single-action hydraulic cylinder of buffer-braking effect piston rod arbitrary position while stopping.
Shown in Figure 2, Fig. 2 is that the utility model hydraulic cylinder piston rod tail end is near the process overall structure schematic diagram of retracting before hydraulic cylinder afterbody buffer cavity.When hydraulic cylinder piston rod 13 afterbodys are retracted near the piston rod before hydraulic cylinder afterbody buffer cavity 5, if the load of its promotion is unchanged, the hydraulic oil in accumulator oil hydraulic cylinder connecting tube 4 is in the state of rest without mobile.If loading on that hydraulic cylinder piston rod 13 promotes increases or reduce, hydraulic oil can or reduce along with the increase of load, by accumulator oil hydraulic cylinder connecting tube 4, is constantly flowed into or is flowed out in accumulator oil-filled chamber 3.Accumulator oil-filled chamber 3 or accumulator inflated with nitrogen chamber 1 promote accumulator piston 2 to the left or to the right ceaselessly mobile maintain nitrogen pressure all the time with induced pressure balance.When hydraulic cylinder piston rod 13 afterbodys are retracted near the piston rod before hydraulic cylinder afterbody buffer cavity 5, due to the fluid pressure difference of steel ball 8 both sides convergence zero still, steel ball 8 is still in cut-off state.Now, hydraulic oil all passes through hydraulic cylinder afterbody buffer cavity 5 and flows out into tubular type hydraulic pressure explosion-proof valve.Load promotes hydraulic cylinder piston rod 13, and hydraulic cylinder piston rod 13 promotes hydraulic cylinder piston 10 and moves right, and hydraulic cylinder piston rod 13 is steadily retracted.
Shown in Figure 3, Fig. 3 is that the utility model hydraulic cylinder piston rod stretches out while starting moment running of hydraulic power oil view.The hydraulic oil being flowed out by tubular type hydraulic pressure explosion-proof valve 20 directly enters the actuator port of oil hydraulic cylinder rodless cavity 9, and hydraulic oil enters rapidly hydraulic cylinder afterbody buffer cavity 5, enters the right-hand member of steel ball 8, by accumulator oil hydraulic cylinder connecting tube 4, enters again in accumulator oil-filled chamber 3.At this moment under the promotion of hydraulic oil, the induced pressure value that is moved to the left nitrogen pressure in accumulator inflated with nitrogen chamber 1 and hydraulic oil is identical just to be stopped.Due to the effect of fluid pressure difference, check valve spring 7 is compressed, and steel ball 8 is moved to the left; Hydraulic oil enters in oil hydraulic cylinder rodless cavity 9 through steel ball 8, check valve spring 7, check valve spring seat 6.The reversing impact of hydraulic oil is sponged by accumulator, and the area that at this moment acts on effective push in hydraulic cylinder afterbody buffer cavity 5 and oil hydraulic cylinder rodless cavity 9 is the useful area of hydraulic cylinder piston 10 just.Like this, hydraulic oil promotes hydraulic cylinder piston 10, and hydraulic cylinder piston 10 is moved to the left promotion hydraulic cylinder piston rod 13 and steadily stretches out, so, this structure guarantees that the moment that piston rod stretches out is the change acceleration startup of non-jitter, has guaranteed that the elevator mechanism that it drives starts the requirement that non-jitter operates steadily.
Shown in Figure 4, Fig. 4 view when to be the utility model hydraulic cylinder piston rod tail end stop near the process arbitrary position of retracting before hydraulic cylinder afterbody buffer cavity.Hydraulic cylinder piston rod 13 afterbodys are when in the piston rod retraction process before hydraulic cylinder afterbody buffer cavity 5, arbitrary position stops, and when selector valve cuts out, hydraulic cylinder piston rod 13 still keeps original inertia.At this moment, the hydraulic oil of hydraulic cylinder afterbody buffer cavity 5 and oil hydraulic cylinder rodless cavity 9 will by accumulator oil hydraulic cylinder connecting tube 4 flow in accumulator oil-filled chambers 3, promote accumulator piston 2 to left movement and in accumulator inflated with nitrogen chamber 1 nitrogen compressed, until the pressure reduction of accumulator inflated with nitrogen chamber 1 and accumulator oil-filled chamber 3 goes to zero, could really stop for locking mechanism.
Shown in Figure 5, Fig. 5 is that the utility model hydraulic cylinder piston rod stretches out after startup to tail end and leaves running of hydraulic power oil view during hydraulic cylinder afterbody buffer cavity.After hydraulic cylinder piston rod 13 starts, if the load of its promotion is unchanged, the hydraulic oil in accumulator oil hydraulic cylinder connecting tube 4 is in the state of rest without mobile.If loading on that hydraulic cylinder piston rod 13 promotes increases or reduces, hydraulic oil can or reduce along with the increase of load, by accumulator oil hydraulic cylinder connecting tube 4, flow into or flow out in accumulator oil-filled chamber 3, accumulator oil-filled chamber 3 or accumulator inflated with nitrogen chamber 1 promote accumulator piston 2 to the left or to the right ceaselessly mobile maintain nitrogen pressure all the time with induced pressure balance.After hydraulic cylinder piston rod 13 starts, check valve spring 7 keeps confined state, and steel ball 8 is motionless; Hydraulic oil enters in oil hydraulic cylinder rodless cavity 9 through steel ball 8, check valve spring 7 and check valve spring seat 6.Meanwhile, hydraulic oil constantly enters in hydraulic cylinder afterbody buffer cavity 5.Like this, hydraulic oil promotes hydraulic cylinder piston 10, and hydraulic cylinder piston 10 is moved to the left promotion hydraulic cylinder piston rod 13 and steadily stretches out.
Shown in Figure 6, Fig. 6 is the utility model hydraulic cylinder piston rod running of hydraulic power oil view while entering after hydraulic cylinder afterbody buffer cavity buffer-braking.After hydraulic cylinder piston rod 13 afterbodys enter hydraulic cylinder afterbody buffer cavity 5, steel ball 8 is in cut-off state.Now, the hydraulic oil in oil hydraulic cylinder rodless cavity 9 can only be by the gap efflux cylinder pressure of 13 of hydraulic cylinder afterbody buffer cavity 5 and hydraulic cylinder piston rods, and it is zero that the effect of gap throttling is reduced to the movement velocity of hydraulic cylinder piston rod 13 gradually.Meanwhile, the hydraulic oil in accumulator is through accumulator oil hydraulic cylinder connecting tube 4 efflux cylinder pressures.
Shown in Figure 7, Fig. 7 is that the utility model hydraulic cylinder piston rod leaves hydraulic cylinder afterbody buffer cavity running of hydraulic power oil view afterwards.After hydraulic cylinder piston rod 13 afterbodys leave hydraulic cylinder afterbody buffer cavity 5, if the load of its thrust is unchanged, the hydraulic oil in accumulator oil hydraulic cylinder connecting tube 4 is in the state of rest without mobile.If loading on that hydraulic cylinder piston rod 13 promotes increases or reduces, hydraulic oil can or reduce along with the increase of load, by accumulator oil hydraulic cylinder connecting tube 4, flow into or flow out in accumulator oil-filled chamber 3, accumulator oil-filled chamber 3 or accumulator inflated with nitrogen chamber 1 promote accumulator piston 2 to the left or to the right ceaselessly mobile maintain nitrogen pressure all the time with induced pressure balance.After hydraulic cylinder piston rod 13 afterbodys leave hydraulic cylinder afterbody buffer cavity 5, because the fluid pressure difference of steel ball 8 both sides levels off to zero, steel ball 8 moves to right at once and blocks former runner under the promotion of check valve spring 7.Now hydraulic oil all passes through hydraulic cylinder afterbody buffer cavity 5 and flows in oil hydraulic cylinder rodless cavity 9.Hydraulic oil promotes hydraulic cylinder piston 10, and hydraulic cylinder piston 10 is moved to the left promotion hydraulic cylinder piston rod 13 and steadily stretches out.
Shown in Figure 8, Fig. 8 is that the utility model hydraulic cylinder piston rod leaves after hydraulic cylinder afterbody buffer cavity view when arbitrary position stops.Hydraulic cylinder piston rod 13 afterbodys leave stretching out in process when arbitrary position stops after hydraulic cylinder afterbody buffer cavity 5, and the hydraulic oil in oil hydraulic cylinder and accumulator remains static at once.
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (6)
1. hydraulic cushion driving, a buffer brake device, is characterized in that, comprises accumulator (16) and oil hydraulic cylinder (17); Described oil hydraulic cylinder (17) comprises hydraulic cylinder (11), hydraulic cylinder piston rod (13) and is assigned in the anterior hydraulic cylinder piston (10) of hydraulic cylinder piston rod (13); In described hydraulic cylinder (11) bottom, is furnished with hydraulically-controlled one-way valve (18); The radial surface of the radial surface of described hydraulic cylinder piston rod (13) afterbody and hydraulic cylinder (11) bottom centre sunk area forms hydraulic cylinder afterbody buffer cavity (5); The port of described hydraulic cylinder afterbody buffer cavity (5) communicates with the oil-feed port of tubular type hydraulic pressure explosion-proof valve, accumulator (16) and hydraulically-controlled one-way valve (18) respectively; The another port of described hydraulically-controlled one-way valve (18) communicates with oil hydraulic cylinder rodless cavity (9).
2. hydraulic cushion driving according to claim 1, buffer brake device, is characterized in that: described accumulator (16) comprises accumulator inflated with nitrogen chamber (1), is placed in accumulator piston (2) and accumulator oil-filled chamber (3) in accumulator; Described accumulator oil-filled chamber (3) communicates with hydraulic cylinder afterbody buffer cavity (5).
3. hydraulic cushion driving according to claim 2, buffer brake device, is characterized in that: described hydraulically-controlled one-way valve (18) comprises check valve spring seat (6), check valve spring (7) and steel ball (8); Described check valve spring (7) is placed on check valve spring seat (6), and the hydraulic oil that hydraulic cylinder afterbody buffer cavity (5) is located enters oil hydraulic cylinder rodless cavity (9) by steel ball (8) and check valve spring seat (6).
4. hydraulic cushion driving according to claim 3, buffer brake device, is characterized in that: the port of described accumulator (16) communicates with the port of hydraulic cylinder afterbody buffer cavity (5) through high pressure hose or seamless steel pipe.
5. hydraulic cushion driving according to claim 4, buffer brake device, is characterized in that: at the upper throttle valve in parallel of described hydraulically-controlled one-way valve (18); One end hydraulic fluid port of described throttle valve communicates with oil hydraulic cylinder rodless cavity (9), and its other end communicates with hydraulic cylinder afterbody buffer cavity (5).
6. hydraulic cushion driving according to claim 1, buffer brake device, is characterized in that: described accumulator (16) adopts bladder type hydropneumatic accumulator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320322031.XU CN203430906U (en) | 2013-06-06 | 2013-06-06 | Hydraulic buffering driving and buffering braking device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320322031.XU CN203430906U (en) | 2013-06-06 | 2013-06-06 | Hydraulic buffering driving and buffering braking device |
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| Publication Number | Publication Date |
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| CN203430906U true CN203430906U (en) | 2014-02-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201320322031.XU Expired - Fee Related CN203430906U (en) | 2013-06-06 | 2013-06-06 | Hydraulic buffering driving and buffering braking device |
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| CN (1) | CN203430906U (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994125A (en) * | 2014-05-20 | 2014-08-20 | 长沙达豪机械设备有限公司 | Adjustable bi-directional buffering oil cylinder |
| CN105402303A (en) * | 2015-12-31 | 2016-03-16 | 河海大学常州校区 | Energy storage buffer |
| CN105422713A (en) * | 2015-12-31 | 2016-03-23 | 河海大学常州校区 | Energy storage buffer |
| CN105422714A (en) * | 2015-12-31 | 2016-03-23 | 河海大学常州校区 | Energy storage buffer |
| CN105443637A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105443638A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105443454A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105972143A (en) * | 2016-05-11 | 2016-09-28 | 庆丰鞋业（江苏）有限公司 | Bearing shock absorber |
| CN108035925A (en) * | 2017-12-04 | 2018-05-15 | 陕西航天动力高科技股份有限公司 | A kind of high reliability buffering throttling oil cylinder connection valve block assembly |
| CN109821163A (en) * | 2019-01-30 | 2019-05-31 | 龙岩学院 | A kind of sense load buffering ramp-down device |
-
2013
- 2013-06-06 CN CN201320322031.XU patent/CN203430906U/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103994125A (en) * | 2014-05-20 | 2014-08-20 | 长沙达豪机械设备有限公司 | Adjustable bi-directional buffering oil cylinder |
| CN103994125B (en) * | 2014-05-20 | 2016-01-13 | 长沙达豪机械设备有限公司 | Adjustable Bidirectional cushion cylinder |
| CN105402303A (en) * | 2015-12-31 | 2016-03-16 | 河海大学常州校区 | Energy storage buffer |
| CN105422713A (en) * | 2015-12-31 | 2016-03-23 | 河海大学常州校区 | Energy storage buffer |
| CN105422714A (en) * | 2015-12-31 | 2016-03-23 | 河海大学常州校区 | Energy storage buffer |
| CN105443637A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105443638A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105443454A (en) * | 2015-12-31 | 2016-03-30 | 河海大学常州校区 | Energy storing type buffer |
| CN105972143A (en) * | 2016-05-11 | 2016-09-28 | 庆丰鞋业（江苏）有限公司 | Bearing shock absorber |
| CN108035925A (en) * | 2017-12-04 | 2018-05-15 | 陕西航天动力高科技股份有限公司 | A kind of high reliability buffering throttling oil cylinder connection valve block assembly |
| CN109821163A (en) * | 2019-01-30 | 2019-05-31 | 龙岩学院 | A kind of sense load buffering ramp-down device |
| CN109821163B (en) * | 2019-01-30 | 2020-07-24 | 龙岩学院 | Load sensing buffering slow descending device |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140212 Termination date: 20180606 |